US6536563B1 - Brake with adjustable play - Google Patents

Brake with adjustable play Download PDF

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Publication number
US6536563B1
US6536563B1 US09/856,329 US85632901A US6536563B1 US 6536563 B1 US6536563 B1 US 6536563B1 US 85632901 A US85632901 A US 85632901A US 6536563 B1 US6536563 B1 US 6536563B1
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United States
Prior art keywords
brake
brake apparatus
base plate
hood
disk
Prior art date
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Expired - Lifetime
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US09/856,329
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English (en)
Inventor
Karl-Heinz Schlehbusch
Burkhard Gärtner
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Pintsch Bubenzer GmbH
Original Assignee
Pintsch Bamag Antriebs und Verkehrstechnik GmbH
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Assigned to PINTSCH BAMAG ANTRIEBS-UND VERKEHRSTECHNIK GMBH reassignment PINTSCH BAMAG ANTRIEBS-UND VERKEHRSTECHNIK GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GARTNER, BURKHARD, SCHLEHBUSCH, KARL-HEINZ
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Publication of US6536563B1 publication Critical patent/US6536563B1/en
Assigned to PINTSCH BUBENZER GMBH reassignment PINTSCH BUBENZER GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PINTSCH BAMAG ANTRIEBS- UND VERKEHRSTECHNIK GMBH
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
    • F16D59/02—Self-acting brakes, e.g. coming into operation at a predetermined speed spring-loaded and adapted to be released by mechanical, fluid, or electromagnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/28—Brakes with only one rotating disc
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/42—Slack adjusters mechanical non-automatic
    • F16D65/46—Slack adjusters mechanical non-automatic with screw-thread and nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/003—Position, angle or speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/20—Electric or magnetic using electromagnets
    • F16D2121/22—Electric or magnetic using electromagnets for releasing a normally applied brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/28—Cams; Levers with cams
    • F16D2125/32—Cams; Levers with cams acting on one cam follower
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/02—Release mechanisms
    • F16D2127/04—Release mechanisms for manual operation

Definitions

  • the invention concerns a brake with a base plate, with which a brake operating device and two brake disks are connected essentially torsion-proof, and with a friction lining arranged to move between the brake disks, connected essentially torsion-proof to an input shaft rotatable relative to the base plate, in which the brake disk facing the base plate is axially moveable and the brake disk facing away from the base plate is axially fixed during operation and kept at a spacing from the axially moving brake disk by a spacer.
  • Such brakes are known from the prior art and are used, for example, for externally and internally ventilated motors in traveling, traversing and hoisting mechanisms on crane units.
  • the base plate is then connected to a fixed object relative to the input shaft, for example, a motor housing.
  • the input shaft is connected to the power cable of the motor and rotates relative to the base plate.
  • the friction lining By activation of the brake operating device, the friction lining is engaged with the brake disk. By friction between the friction lining rotating with the input shaft and the brake disk, rotation of the input shaft relative to the brake plate is braked and/or stopped.
  • the spacer serves as a stop for the brake disk so that during release of the brake, the friction lining can be released from the brake disk.
  • a brake of this type is disclosed in German patent document no. DE 2 660 855 C2.
  • the base plate of the brake disclosed in this German document forms a friction surface.
  • the actuating device and moveable brake disk are held at a distance from the base plate by a spacer sleeve.
  • the brake in DE 2 660 855 C2 requires removal of the actuating device and the moveable brake disk when the friction lining is to be replaced.
  • the ordinary brakes have the drawbacks that they can only be maintained with difficulty. During maintenance, several housing parts must often be removed from the brake in time-consuming fashion and the brake taken out of service. Moreover, brake disks and friction linings of ordinary brakes wear very quickly in crane installations, in harbor use or on ships, which requires frequent maintenance. On wear of the friction lining, this becomes thinner and the looseness of the brake changes. In order to keep the braking torque constant in friction linings that are becoming thinner, the brake clearance of the brake must often be readjusted. Adjustment of the brake clearance is very labor- and time-intensive in ordinary brakes and therefore connected with high cost.
  • the underlying task of the present invention is to devise a brake which, in comparison with ordinary brakes, permits a very simple possibility for adjustment of the brake clearance.
  • a second brake disk is employed that faces away from the brake plate.
  • the second brake disk is connected to the brake operating device in a torsion-proof manner, i.e., it is not rotatable relative to the operating device.
  • a friction lining disk is positioned between the two brake disks, and the brake operating device is positioned between base plate and the two brake disks.
  • the second brake disk is held in position by a spacer and fastening screw.
  • the spacer is adjustable in an axial direction of the brake so that the free gap between the two brake disks is adjustable.
  • This solution is technically simple and has the advantage that the stop for the brake disk is moveable in the axial direction because of the axial adjustability of the spacer. In this manner, the brake clearance can be rapidly adjusted without considerable time expense. Since the spacer is also arranged, like the operating device, on the base plate, the brake disk need not be removed from the base plate to adjust the brake clearance.
  • the spacer can be connected to the operating device. Since the brake disk is connected to the brake operating device and this is connected to the base plate, a design unit is formed in this manner that need not be disassembled during adjustment of the brake clearance.
  • This embodiment is also particularly advantageous when the brake is disengaged by a force exerted by the operating device, for example, a magnetic force. In this case, the brake disk is supported on the spacer during disengagement and power flow is guided directly back into the brake operating device during disengagement.
  • the spacer can be provided at least in the region between the brake disks with a hexagon insert.
  • the brake clearance can be adjusted particularly easily with a corresponding wrench of pliers.
  • Other key forms of the spacer are also possible, which offer a similar adjustment possibility, for example, other polygonal shapes or holes distributed on the periphery.
  • the spacer can have outside threading.
  • the outside thread is cost-effective and simple to manufacture and permits precise adjustment of the brake clearance.
  • the external thread can advantageously also be configured self-inhibiting in order to prevent displacement of the spacer and thus the brake clearance during operation of the brake.
  • the brake disk can be fastened to the base plate with a fastening screw, in which the fastening screw extends through the spacer.
  • Optimal power flow in the brake is obtained if, in another advantageous embodiment, the fastening screw is connected to the base plate.
  • the braking force exerted on the fastening screw by the brake disk is directly introduced to the base plate on this account.
  • the housing can be designed as a bell-shaped hood, which is supported sealed on the base plate and forms a brake interior sealed water-tight at least relative to the surrounding of the brake, in which the brake operating device, the friction lining and the brake disk are accommodated.
  • This has the advantage that the brake is easier to maintain because of the bell-shaped housing than ordinary brakes. All essential components of the brake are arranged in the bell-shaped housing with the brake operating device, the friction lining and the brake disk, which can be subject to wear and/or must be regularly maintained. During removal of the bell-shaped hood, these components are freely accessible. The brake remains functional despite the removed hood, since the brake cooperating device, the brake disk and the friction lining are connected to the base plate. In this manner, the function of the brake can be easily checked during maintenance work.
  • a sealing element can be arranged between the base plate and hood.
  • This modification leads to lower manufacturing costs, since precisely adjacent and flush sealing surfaces of the base plate and hood can be dispensed with. Such sealing surfaces must satisfy high tolerance requirements.
  • sealing elements are easy to introduce and compensate for irregularities in the supporting surfaces of the base plate and hood.
  • this sealing element can be designed as an O-ring.
  • the embodiment of the brake with a watertight sealing of the brake interior is advantageous, independently of the viewpoint of the configuration of the fastening screw and spacer, so that independent protection is sought for this embodiment.
  • the hood can be connected to the brake operating device.
  • no fastening devices need be provided on the base plate for the brake operating device.
  • the base plate can, therefore, be designed as tight plate having no openings through which liquid can penetrate into the brake interior. If the brake operating device and/or the brake disk are connected to the base plate, a design is obtained in which the hood can be easily removed from the brake and operation of the brake is guaranteed particularly simply with the hood removed. It should be kept in mind that the brake disk is axially moveable relative to the base plate in order to permit engagement and disengagement (release) of the brake.
  • the bearing points of the brake disk and/or brake operating device are situated exclusively on the base plate. In this case, during loosening of the hood, the brake disk and/or brake operating device remain on the base plate. This also leads to a very simple design configuration of the hood and to a possibility of maintenance of the brake with the hood removed.
  • Additional devices can be connected to the input shaft when, in an additional advantageous embodiment of the brake, a flange essentially coaxial to the input shaft is formed on the outside of the hood with a through opening coaxially to the input shaft.
  • the coaxial flange permits attachment of the additional devices to the hood.
  • the coaxial through openings permit lengthening of the input shaft through the brake.
  • a continuous maintenance opening can be provided which can be closed airtight and/or watertight with a closure element.
  • the maintenance opening can then be arranged on the periphery of the hood in the radial direction relative to the input shaft. Because of the radial shape of the opening, condensation water automatically runs off the maintenance opening situated on the bottom. Moreover, the thickness of the friction lining and brake disk can be inspected through the maintenance openings.
  • the maintenance opening which runs parallel to the input shaft, can be advantageous for manual release of the brake and has a condensation water discharge hole in a vertical incorporation position.
  • the maintenance opening is expediently designed as a threaded hole, which is preferably closed water- or airtight by a closure screw.
  • the closure screw can have sealing elements, like O-rings, which lead to a particularly tight closure of the threaded hole.
  • a manual disengagement device that is moveable relative to the hood, which can be transferred to a disengagement position.
  • the brake is released in the disengagement position.
  • the manual disengagement device is mechanically and/or hydraulically connected to the brake disk and/or friction lining.
  • the force applied to the brake disk and/or friction lining by the manual disengagement device is preferably greater than the force applied by the brake operating device so that during defective function of the brake operating device, the brake can be released by the manual disengagement device.
  • the manual disengagement device is designed as a lever, which is mounted to pivot on the hood on at least one bearing. High forces for release can be introduced to the brakes by a lever without having to incur high design costs.
  • the bearing can be provided in another advantageous embodiment with at least one bearing seal, through which the bearing is sealed watertight and/or airtight.
  • a particularly loadable bearing of the manual disengagement device on the hood is obtained if, in another advantageous embodiment, two bearings are provided on two essentially opposite positions of the hood relative to the input shaft and to each other. With this embodiment, very large forces can be introduced into the brake without the hazard of damage to the bearing.
  • an axially moveable disengagement device can be provided through which one brake disk can be moved in a direction away from the other brake disk and the brake disengaged on this account, during which the one brake disk is held at least indirectly by the disengagement device on the base plate when the other brake disk and/or friction lining is removed.
  • the disengagement device therefore fulfills a dual function in which it serves for both release of the brake and also as a maintenance aid, through which the one brake disk can be kept on the brake during maintenance work and need not be disassembled from the brake.
  • the embodiment of the brake with the disengagement means and disengagement device for manual disengagement of the brake are advantageous independently of the viewpoint of a watertight sealing of the brake interior, so that independent protection is also sought for this embodiment.
  • a brake can have an electronic monitoring device, which is preferably arranged within the hood and through which a signal can be released that represents the function and/or wear of the brake.
  • This electronic monitoring device can be designed, for example, in the form of a microswitch and/or in the form of a proximity switch.
  • the microswitch like the proximity switch, is capable of recording engagement of the brake or issuing a signal when the thickness of the friction lining falls short of a minimum. This signal can be required, for example, for maintenance purposes in order to be able to establish without intervention on the brake when the friction lining or brake disk must be replaced.
  • FIG. 1 shows the first practical example of the brake according to the invention in a view on one face of the hood
  • FIG. 2 shows a cross section along line II—II of FIG. 1;
  • FIG. 3 shows a cross section through a disengagement device according to the first practical example
  • FIG. 4 shows a second practical example of the brake according to the invention in a front view on the hood
  • FIG. 5 shows a sectional view of the second practical example of the brake according to the invention in a section along a center axis of the brake
  • FIG. 6 shows a detail A of FIG. 3 in cross section.
  • FIG. 2 shows a section along line II—II of FIG. 1 .
  • the brake 1 has a base plate 2 , on which a brake operating device 4 is fastened via several screws 3 distributed on the periphery.
  • the brake operating device 4 has an electromagnet 5 and a spring element 6 configured as a compression spring.
  • the compression spring 6 is supported between the brake operating device 4 and a brake disk 7 .
  • the brake 1 also has an input shaft 8 , which is connected to rotate in unison by means of tapered toothing to a friction lining 9 whose diameter is less than that of brake disk 7 .
  • the friction lining 9 is arranged between the one brake disk 7 and another break disk 10 and, thanks to the tapered toothing, is moveable in the axial direction on the input shaft 8 .
  • the brake disks 7 , 10 are also moveable in the axial direction of the brake on three screws 11 distributed on the periphery.
  • the brake disks 7 , 10 do not have the same diameter.
  • the brake operating device 4 , the two brake disks 7 , 10 and the friction lining 9 run coaxially to each other and to a center line M of the input shaft of the input shaft 8 , which simultaneously forms the center line of brake 1 .
  • the screw heads of screws 11 simultaneously serve as axial stop for adjustment of the clearance of the brake.
  • the screws 11 extend through brake disk 7 and brake operating device 4 and are screwed to the base plate 2 .
  • the brake operating device 4 is provided with a corresponding through opening for each screw 11 , which has a threaded section with greater diameter for the brake disks 7 , 10 .
  • a sleeve 12 is arranged in the threaded section of the brake operating device 4 , which extends through the first brake disk 7 . Since the second brake disk 10 is provided with a smaller opening, the sleeve 12 is supported in the axial direction on the second outer brake disk 10 .
  • the sleeve has an external threading on the section positioned in the direction of the base plate 2 , which is screwed into the threaded section of the operating device 4 .
  • the section of sleeve 12 in contact with brake disk 10 is designed as a hexagon.
  • sleeve 12 is secured with slight play so that it is mounted rotatable, on the one hand, and can support the brake disk 7 in the peripheral direction, on the other.
  • the threaded hole to receive screw 11 of base plate 2 is shown continuous in the first practical example, but can also be designed as a blind hole so that the back side of base plate 2 facing away from brake operating device 4 and brake disks 7 , 10 is sealed.
  • base plate 2 is ordinarily fastened to an electric motor (not shown), whose motor shaft drives the input shaft 8 of brake 1 , for example, via an adjusting spring.
  • Fastening openings 13 to receive corresponding screws are provided on base plate 2 to fasten brake 1 to the electric motor.
  • the braking torque is fed to the housing of the electric motor via base plate 2 .
  • the fastening opening 13 can also be designed closeable or as a blind hole.
  • the threaded hole for screw 3 which connects base plate 2 to the brake operating device 4 , can also be configured as a blind hole.
  • the brake operating device 4 , the two brake disks 7 , 10 and the friction lining 9 are accommodated in a bell-shaped hood 14 , which is supported tight against the base plate 2 .
  • an O-ring 15 is arranged to the sealing element between base plate 2 and hood 14 .
  • Hood 14 is screwed to the brake operating device 4 by means of three screws 16 distributed on the periphery and therefore indirectly connected to base plate 2 .
  • the screws 16 extend in the axial direction outside of electromagnet through the two brake disks 7 , 10 .
  • the screws 16 lie on the same diameter as screws 11 .
  • the screws 11 take up part of the braking torque and convey it to base plate 2 via the brake operating device 4 .
  • the screw heads of screws 16 lie in recesses on the front surface 17 of the hood. These recesses have internal threading into which the closure screws 18 are screwed. These closure screws seal the recesses in the hood and the through openings for the screws 16 situated behind them.
  • the brake interior 19 in which the brake operating device 4 , the brake disks 7 , 10 and the friction lining 9 are accommodated, is sealed in a brake 1 screwed to an electric motor.
  • Radially running maintenance openings are provided on the axially extending peripheral surface 20 of the hood, which are closed water- and airtight by screws 21 .
  • the screws 21 are provided with seals for this purpose.
  • the closure screw 21 depicted in FIG. 2 is arranged on the bottom in the depicted position of incorporation.
  • the maintenance opening closed by it serves as a condensation water discharge.
  • the first practical example of brake 1 has a through opening 22 running coaxially to the center line M of the brake, which is enclosed by a flange section 23 .
  • the input shaft 8 likewise has fastening devices 24 on its end facing away from base plate 2 and the electric motor, on which another shaft can be fastened, which passes through opening 22 .
  • a tachometer (not shown) can be mounted on the shaft, for example.
  • a transitional flange for a watertight connection of the brakes to a tachometer housing can be mounted on flange 23 .
  • the flange section 23 is machined flat so that easy sealing of this surface is possible.
  • a terminal box 25 which serves for watertight connection of the operating cable for electromagnet 5 and additional electrical devices for wear monitoring, like proximity switches (not shown) is shown in FIG. 2 with a dashed line.
  • FIG. 1 shows a front view of brake 1 on the hood side. It is apparent here that the terminal box 25 is offset laterally with the cable mounts in the depicted incorporation position for condensation water discharge 21 . Moreover, two additional maintenance openings are provided on peripheral surface 20 in hood 14 , which are closed water- and airtight with closure screws 26 , 27 . These two maintenance openings are arranged in the axial direction at the height of friction lining 9 and serve as inspection openings to check the abrasion of the friction lining 9 .
  • Two additional diametrically opposite maintenance openings on the front 17 of hood 2 are also closed water- and airtight by closure screws 28 , 29 . These openings serve as access openings for a manual release device, which can be seen in FIG. 3 .
  • the brake disks 7 , 10 are provided with two additional through openings whose position corresponds to the maintenance openings closed by the closure screws 28 , 29 .
  • Screws 28 ′ are mounted between operating element 4 and the first brake disk 7 behind these through openings, which are accessible through the maintenance openings 28 , 29 .
  • the components that correspond in function to the components of the first practical example are provided with the same reference numbers. Explanation of these components is dispensed with in describing the second practical example.
  • the second practical example in contrast to the first practical example, does not prescribe the connection of an additional shaft for connection of additional devices to the input shaft 8 . Consequently, the hood 2 of the second practical example has no flange 23 and no opening 22 .
  • the input shaft 8 has no fastening capability 24 .
  • the front surface 17 of hood 2 is provided with a maintenance opening 28 that runs coaxially to the center line M, which serves as a condensation water discharge 28 in a vertical incorporation position.
  • This maintenance opening 28 is also closed water-and airtight by a closure screw.
  • the second practical example also has a manual disengagement device in the form of a lever 29 , which is mounted on two bearings 31 in the axial direction of brake 1 to pivot via fork 30 which partially encloses the peripheral surface 20 of the hood.
  • a manual disengagement device in the form of a lever 29 , which is mounted on two bearings 31 in the axial direction of brake 1 to pivot via fork 30 which partially encloses the peripheral surface 20 of the hood.
  • One of the two bearings 31 is shown as detail A in FIG. 6 in section. Bearings 31 are configured watertight so that no water can penetrate into the brake interior 19 through them.
  • the fork 30 is connected torsion-proof to a shaft 33 via a shape mating secured by a screw 32 .
  • This shape mating is achieved by an external hexagon insert placed on the end of the shaft, which engages in a corresponding internal hexagon insert of lever 30 .
  • Screw 32 secures this connection in the axial direction of shaft 33 .
  • the coupling is released, i.e., the friction lining 9 is forced away from the first brake disk 7 . This can occur, for example, by a cam device or a lever on the end of the shaft so that the brake disk 7 is moved in the direction of the operating device against the action of springs 6 .
  • a sealing element 34 in this case an O-ring is arranged between shaft 33 and hood 17 .
  • the bearings 31 are sealed against penetration of water into the brake interior 19 by the sealing element 34 .
  • lever 29 Through a force K that acts on lever 29 , this can be pivoted in the axial direction.
  • a screw 36 secured in a nut on lever 29 is supported on the periphery 20 of brake 1 and serves as stop.
  • the screw 36 also serves to fix the lever 29 in the disengagement position, which is shown with a dashed line in FIG. 4 .
  • the brake 1 is related in the disengagement position.
  • the lever 29 can be moved with greater force into the disengagement position by tightening screw 26 .
  • the function of the brake according to the invention is outlined below.
  • the brake disk 7 is pulled by the action of the magnetic field in the direction of the operating device 4 , i.e., against the force direction of spring 6 . Since the brake disk 10 is fixed in the axial direction, it cannot follow the movement of the brake disk 7 , so that the brake is released on engagement of electromagnet 5 .
  • hood 14 is therefore releasable from base plate 2 .
  • the brake disks 7 , 10 are also connected to the operating device 4 and the base plate 2 via screws 3 and sleeve 12 when the hood 14 is removed.
  • the brake 1 is therefore also completely functional and easy to maintain with the hood 14 removed.
  • a watertight sealing of the brake interior 19 which can also be designed airtight with appropriate modification of the seals known to one skilled in the art, is achieved by seal 15 and by the watertight closure screws 18 , 21 , 26 , 27 , 28 , 29 on the hood.
  • the base plate 2 has only blind holes instead of through openings, tightness can be achieved by the brake according to the invention without additional expedients that withstands pressures up to 100 mbars (1 mH 2 O). This corresponds to protection class IP 67.
  • the brake according to the invention is therefore corrosion-resistant in the maritime and tropical area. Special protective precautions for moisture-sensitive components, therefore, need not be incorporated in the brake interior 19 . These include, for example, electronic monitoring devices, which monitor the thickness of the brake disks between the brake disks 7 , 10 and/or the friction lining 9 or engagement of brake 1 . These monitoring devices are microswitches or proximity switches.
  • the brake 1 in the first practical example can be released by the manual release depicted in FIG. 3 .
  • the screw 28 ′ as shown in FIG. 3, is supported in the state loosened as far as possible on brake disk 10 so that it sits fixed during operation of brake 1 .
  • the hole 28 ′ of brake disk 10 flush with screw 28 ′′ expediently has a smaller diameter than the screw head of screw 28 ′.
  • the closure screw 28 is initially loosened and then a wrench is placed through the maintenance opening and opening 28 ′′ and the screw 28 ′ is tightened in the direction of brake disk 7 into the fastening device 4 . In this manner the brake disk 7 is moved in the direction of the fastening device against the spring action of spring 6 and the brake is manually released.
  • the screw 28 ′ also holds the brake disk 7 against the pressure of spring 6 against the operating device 4 during maintenance of brake 1 . After loosening the screw 16 and 11 , the brake disk 10 and the friction line 9 can therefore be rapidly removed in a manner suitable for maintenance, since they are no longer under the action of spring force.
  • the brake is released by operating lever 29 .
  • the lever is forced in the axial direction away from base plate 2 .
  • a water resistance to 100 mbars (1 mH 2 O) can be achieved, i.e., a protection class IP 67.
  • a protection class IP 67 because of the bell-shaped hood 14 and the arrangement of the components of brake 1 on base plate 2 , easy maintenance is possible without having to disassemble brake 1 from the electric motor or to dismantle brake 1 or brake disks 7 , 10 or the brake operating device 4 from the base plate 2 and the friction lining 9 from the input shaft 8 .
  • Abrasion of the friction lining 9 is compensated by axial displacement of brake disk 10 by means of sleeve 12 and screw 11 so that the clearance of brake 1 remains essentially constant.
  • the sleeve 12 is initially screwed further into the fastening device.
  • Sleeve 12 serves as a stop in the axial direction in the direction of operating device 4 . If this stop is displaced in the direction of the operating device or in the direction of the friction lining, the brake disk 10 migrates closer to the other brake disk 7 and the gap between the two brake disks is reduced. In this manner the original brake clearance is restored and the abrasion of the friction lining 9 is compensated.
  • Screw 11 is then retightened so that the brake disk 10 is clamped fixed between sleeve 12 and screw 11 .
  • the external hexagon insert of sleeve 12 in the region of the gap between the two brake disks 7 , 10 facilitates tightening of sleeve 12 .
  • the two depicted practical examples of brake 1 each represent an electromagnetic two-faced spring-loaded brake, which is ordinarily designed for braking torques between 100 Nm and 1600 Nm.
  • the base plate is designed as a normal flange with diameters between 200 mm and 800 mm.
  • the hood 12 is made from cast iron.
  • the depicted brakes are used, for example, as crane brakes on ships and in harbors.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Braking Arrangements (AREA)
US09/856,329 1998-11-20 1999-11-22 Brake with adjustable play Expired - Lifetime US6536563B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE29820814U DE29820814U1 (de) 1998-11-20 1998-11-20 Bremse mit Spielverstellung
DE29820814U 1998-11-20
PCT/EP1999/008983 WO2000031432A1 (de) 1998-11-20 1999-11-22 Bremse mit spielverstellung

Publications (1)

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US6536563B1 true US6536563B1 (en) 2003-03-25

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Family Applications (1)

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US09/856,329 Expired - Lifetime US6536563B1 (en) 1998-11-20 1999-11-22 Brake with adjustable play

Country Status (4)

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US (1) US6536563B1 (de)
EP (1) EP1131566A1 (de)
DE (1) DE29820814U1 (de)
WO (1) WO2000031432A1 (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060153004A1 (en) * 2004-02-04 2006-07-13 Andrey Berg System for geophysical prospecting using induced electrokinetic effect
US20070175712A1 (en) * 2006-01-28 2007-08-02 Jungheinrich Aktiengesellschaft Spring brake for an industrial truck
US20080202872A1 (en) * 2007-02-22 2008-08-28 Hung Ping Huang Handle of electromagnetic brake
US20090166136A1 (en) * 2006-04-07 2009-07-02 Chr. Mayr Gmbh & Co, Kg Rectangular, electromagnetically releasing dual-circuit spring-pressure brake
US20090260927A1 (en) * 2008-04-16 2009-10-22 Yesheng Qu Disk brake
CN102797774A (zh) * 2011-05-24 2012-11-28 上海三嵩精密机电有限公司 用于车库的密闭式刹车装置
CN103066793A (zh) * 2011-10-20 2013-04-24 上海三嵩精密机电有限公司 双电压交流电磁煞车器
CN104870853A (zh) * 2012-11-28 2015-08-26 索尤若驱动有限及两合公司 制动装置和电机
US20150345571A1 (en) * 2013-02-19 2015-12-03 Koh Young Technology Inc. Magnetic brake
US10298092B2 (en) * 2014-12-16 2019-05-21 Siemens Aktiengesellschaft Dynamo-electric machine with a brake
US10975927B2 (en) * 2018-08-17 2021-04-13 Otis Elevator Company Brake device for elevator and an elevator system
US20220080938A1 (en) * 2020-09-15 2022-03-17 Doosan Corporation Electromagnetic brake system

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29820822U1 (de) * 1998-11-20 1999-02-04 Pintsch Bamag Ag Bremse mit manueller Lüfteinrichtung
DE29820821U1 (de) * 1998-11-20 1999-02-04 Pintsch Bamag Ag Wasserdichte Bremse
EP1409885A1 (de) * 2001-02-21 2004-04-21 Group Newtech International Inc. Bremse mit verschleissnachstellvorrichtung
CN106460970B (zh) * 2014-06-24 2018-08-31 谐波传动系统有限公司 无励磁工作制动器以及带无励磁动作制动器的电动机
WO2018041323A1 (de) * 2016-09-02 2018-03-08 Auma Riester Gmbh & Co. Kg Bremsvorrichtung und bremsverfahren

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US2543830A (en) 1945-10-17 1951-03-06 Standard Dayton Corp Electromagnetic brake device
US3357528A (en) * 1965-05-21 1967-12-12 Verlinde Sa Electromagnetic disc brake for electric motor
DE2242073A1 (de) 1972-08-26 1974-03-07 Brinkmann Karl Ernst Elektromagnetisch lueftbare federdruckbremse
FR2319232A1 (fr) 1975-07-23 1977-02-18 Acec Moteur-frein
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DD148250A1 (de) 1979-12-21 1981-05-13 Heinrich Gebers Elektromagnetisch schaltbare reibungsbremse
US4280073A (en) * 1979-03-01 1981-07-21 Facet Enterprises, Inc. Electromagnetically released spring applied friction brake with torque booster
US4299857A (en) * 1978-12-06 1981-11-10 Velasco Jr Ralph E Method for producing corn masa
DE2660855C2 (de) 1976-06-10 1985-01-17 Karl-Ernst 4924 Barntrup Brinkmann Nachstellvorrichtung für eine elektromagnetisch lüftbare Federdruckbremse
DE3338289A1 (de) 1983-10-21 1985-05-02 Maschinenfabrik Stromag Gmbh, 4750 Unna Federdruckbetaetigte und elektromagnetisch lueftbare reibbremse
US4966255A (en) * 1988-11-16 1990-10-30 Reliance Electric Industrial Company Automatic wear compensator for electromagnetic brake
DE3920148A1 (de) 1989-06-20 1991-01-10 Mayr Christian Gmbh & Co Kg Nachstellvorrichtung fuer eine elektromagnetisch lueftbare federdruckbremse
US5154261A (en) * 1989-08-18 1992-10-13 Hitachi, Ltd. Electromagnetic disc brake for elevator lifting apparatus
EP0520727A1 (de) 1991-06-25 1992-12-30 Shinko Denki Kabushiki Kaisha Reibungskraft-Übertragungseinrichtung zur Verwendung in Vakuum
GB2302574A (en) 1995-06-23 1997-01-22 Mayr Christian Gmbh & Co Kg Electrically operated brake
DE19819141A1 (de) * 1997-05-01 1998-12-03 Stromag Ag Elektromagnetische Federdruckbremse
DE29820822U1 (de) 1998-11-20 1999-02-04 Pintsch Bamag Ag Bremse mit manueller Lüfteinrichtung
US6237730B1 (en) * 1997-07-31 2001-05-29 Chr. Mayr Gmbh & Co. Kg Friction safety brake having two independent braking circuits

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US2543830A (en) 1945-10-17 1951-03-06 Standard Dayton Corp Electromagnetic brake device
US3357528A (en) * 1965-05-21 1967-12-12 Verlinde Sa Electromagnetic disc brake for electric motor
DE2242073A1 (de) 1972-08-26 1974-03-07 Brinkmann Karl Ernst Elektromagnetisch lueftbare federdruckbremse
FR2319232A1 (fr) 1975-07-23 1977-02-18 Acec Moteur-frein
DE2660855C2 (de) 1976-06-10 1985-01-17 Karl-Ernst 4924 Barntrup Brinkmann Nachstellvorrichtung für eine elektromagnetisch lüftbare Federdruckbremse
US4136634A (en) * 1977-11-14 1979-01-30 Eaton Corporation Hoist brake wear indicator
US4299857A (en) * 1978-12-06 1981-11-10 Velasco Jr Ralph E Method for producing corn masa
US4280073A (en) * 1979-03-01 1981-07-21 Facet Enterprises, Inc. Electromagnetically released spring applied friction brake with torque booster
DD148250A1 (de) 1979-12-21 1981-05-13 Heinrich Gebers Elektromagnetisch schaltbare reibungsbremse
DE3338289A1 (de) 1983-10-21 1985-05-02 Maschinenfabrik Stromag Gmbh, 4750 Unna Federdruckbetaetigte und elektromagnetisch lueftbare reibbremse
US4966255A (en) * 1988-11-16 1990-10-30 Reliance Electric Industrial Company Automatic wear compensator for electromagnetic brake
DE3920148A1 (de) 1989-06-20 1991-01-10 Mayr Christian Gmbh & Co Kg Nachstellvorrichtung fuer eine elektromagnetisch lueftbare federdruckbremse
US5154261A (en) * 1989-08-18 1992-10-13 Hitachi, Ltd. Electromagnetic disc brake for elevator lifting apparatus
EP0520727A1 (de) 1991-06-25 1992-12-30 Shinko Denki Kabushiki Kaisha Reibungskraft-Übertragungseinrichtung zur Verwendung in Vakuum
US5515953A (en) * 1991-06-25 1996-05-14 Shinko Denki Kabushiki Kaisha Frictional force transmitting device used in vacuum
GB2302574A (en) 1995-06-23 1997-01-22 Mayr Christian Gmbh & Co Kg Electrically operated brake
DE19819141A1 (de) * 1997-05-01 1998-12-03 Stromag Ag Elektromagnetische Federdruckbremse
US6237730B1 (en) * 1997-07-31 2001-05-29 Chr. Mayr Gmbh & Co. Kg Friction safety brake having two independent braking circuits
DE29820822U1 (de) 1998-11-20 1999-02-04 Pintsch Bamag Ag Bremse mit manueller Lüfteinrichtung

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Article from "Trade and Industry News" entitled Baureihe aus Dresden, vol. 47, No. 10, Oct. 1, 1995, p. 64.

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060153004A1 (en) * 2004-02-04 2006-07-13 Andrey Berg System for geophysical prospecting using induced electrokinetic effect
US20070175712A1 (en) * 2006-01-28 2007-08-02 Jungheinrich Aktiengesellschaft Spring brake for an industrial truck
US8550219B2 (en) * 2006-04-07 2013-10-08 Chr. Mayr Gmbh & Co. Kg Rectangular, electromagnetically releasing dual-circuit spring-pressure brake
US20090166136A1 (en) * 2006-04-07 2009-07-02 Chr. Mayr Gmbh & Co, Kg Rectangular, electromagnetically releasing dual-circuit spring-pressure brake
US20080202872A1 (en) * 2007-02-22 2008-08-28 Hung Ping Huang Handle of electromagnetic brake
US7926629B2 (en) * 2007-02-22 2011-04-19 Ya Cheng Electrical Engineering Co., Ltd. Handle of electromagnetic brake
US20090260927A1 (en) * 2008-04-16 2009-10-22 Yesheng Qu Disk brake
US8091691B2 (en) * 2008-04-16 2012-01-10 Suzhou Torin Drive Equipment Co., Ltd. Disk brake
CN102797774A (zh) * 2011-05-24 2012-11-28 上海三嵩精密机电有限公司 用于车库的密闭式刹车装置
CN103066793A (zh) * 2011-10-20 2013-04-24 上海三嵩精密机电有限公司 双电压交流电磁煞车器
CN104870853A (zh) * 2012-11-28 2015-08-26 索尤若驱动有限及两合公司 制动装置和电机
US20150292580A1 (en) * 2012-11-28 2015-10-15 Sew-Eurodrive Gmbh & Co. Kg Brake System and Electric Motor
US9903430B2 (en) * 2012-11-28 2018-02-27 Sew-Eurodrive Gmbh & Co. Kg Brake system and electric motor
CN104870853B (zh) * 2012-11-28 2019-03-29 索尤若驱动有限及两合公司 制动装置和电机
US20150345571A1 (en) * 2013-02-19 2015-12-03 Koh Young Technology Inc. Magnetic brake
US10298092B2 (en) * 2014-12-16 2019-05-21 Siemens Aktiengesellschaft Dynamo-electric machine with a brake
US10975927B2 (en) * 2018-08-17 2021-04-13 Otis Elevator Company Brake device for elevator and an elevator system
US20220080938A1 (en) * 2020-09-15 2022-03-17 Doosan Corporation Electromagnetic brake system
US11845412B2 (en) * 2020-09-15 2023-12-19 Doosan Industrial Vehicle Co., Ltd. Electromagnetic brake system

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DE29820814U1 (de) 1999-02-04
EP1131566A1 (de) 2001-09-12
WO2000031432A1 (de) 2000-06-02

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